8-Speed Transmission

ABSTRACT

The transmission has a plurality of members that can be utilized in powertrains to provide at least eight forward speed ratios and at least one reverse speed ratio. The transmission includes four planetary gear sets having five torque-transmitting devices, three fixed interconnections and a grounded member. The powertrain includes an engine and torque converter that is continuously connected to at least one of the planetary gear members and an output member that is continuously connected with another one of the planetary gear members. The five torque-transmitting devices provide interconnections between various gear members, and with a stationary member, and are operated in combinations of two to establish at least eight forward speed ratios and at least one reverse speed ratio.

CROSS REFERENCE TO RELATED APPLICATION

This application claims the benefit of U.S. Provisional PatentApplication No. 60/912,963, filed Apr. 20, 2007, and which is herebyincorporated by reference in its entirety.

TECHNICAL FIELD

The present invention relates to a power transmission having fourplanetary gear sets that are controlled by five torque-transmittingdevices to provide at least eight forward speed ratios and at least onereverse speed ratio.

BACKGROUND OF THE INVENTION

Passenger vehicles include a powertrain that is comprised of an engine,multi-speed transmission, and a differential or final drive. Themulti-speed transmission increases the overall operating range of thevehicle by permitting the engine to operate through its torque range anumber of times. The number of forward speed ratios that are availablein the transmission determines the number of times the engine torquerange is repeated. Early automatic transmissions had two speed ranges.This severely limited the overall speed range of the vehicle andtherefore required a relatively large engine that could produce a widespeed and torque range. This resulted in the engine operating at aspecific fuel consumption point during cruising, other than the mostefficient point. Therefore, manually-shifted (countershafttransmissions) were the most popular.

With the advent of three- and four-speed automatic transmissions, theautomatic shifting (planetary gear) transmission increased in popularitywith the motoring public. These transmissions improved the operatingperformance and fuel economy of the vehicle. The increased number ofspeed ratios reduces the step size between ratios and therefore improvesthe shift quality of the transmission by making the ratio interchangessubstantially imperceptible to the operator under normal vehicleacceleration.

Six-speed transmissions offer several advantages over four- andfive-speed transmissions, including improved vehicle acceleration andimproved fuel economy. While many trucks employ power transmissionshaving six or more forward speed ratios, passenger cars are stillmanufactured with three- and four-speed automatic transmissions andrelatively few five- or six-speed devices due to the size and complexityof these transmissions.

Seven-, eight- and nine-speed transmissions provide further improvementsin acceleration and fuel economy over six-speed transmissions. However,like the six-speed transmissions discussed above, the development ofseven-, eight- and nine-speed transmissions has been precluded becauseof complexity, size and cost.

SUMMARY OF THE INVENTION

The present invention provides an improved transmission having fourplanetary gear sets controlled to provide at least eight forward speedratios and at least one reverse speed ratio.

The transmission family of the present invention has four planetary gearsets, each of which includes a first, second and third member, whichmembers may comprise a sun gear, a ring gear, or a planet carrierassembly member, in any order.

In referring to the first, second, third and fourth gear sets in thisdescription and in the claims, these sets may be counted “first” to“fourth” in any order in the drawing (i.e., left to right, right toleft, etc.). Additionally, the first, second or third members of eachgear set may be counted “first” to “third” in any order in the drawing(i.e., top to bottom, bottom to top, etc.) for each gear set.

Each carrier member can be either a single-pinion carrier member(simple) or a double-pinion carrier member (compound). Embodiments withlong pinions are also possible.

A first interconnecting member continuously connects the third member ofthe first planetary gear set with the first member of the secondplanetary gear set.

A second interconnecting member continuously connects the third memberof the second planetary gear set with the second member of the thirdplanetary gear set and with the third member of the fourth planetarygear set.

A third interconnecting member continuously connects the third member ofthe third planetary gear set with the second member of the fourthplanetary gear set.

The first member of the first planetary gear set is continuouslyconnected with the stationary member (transmission housing/casing).

The input member is continuously connected with the second member of thefirst planetary gear set. The output member is continuously connectedwith the second member of the second planetary gear set.

A first torque-transmitting device, such as a brake, selectivelyconnects the first member of the third planetary gear set with astationary member (transmission housing/casing).

A second torque-transmitting device, such as a brake, selectivelyconnects the third member of the third planetary gear set with astationary member (transmission housing/casing).

A third torque-transmitting device, such as a clutch, selectivelyconnects the second member of the first planetary gear set with thethird member of the third planetary gear set.

A fourth torque-transmitting device, such as a clutch, selectivelyconnects the third member of the first planetary gear set with the firstmember of the fourth planetary gear set.

A fifth torque-transmitting device, such as a clutch, selectivelyconnecting the second member of the second planetary gear set with thefirst member of the fourth planetary gear set.

The five torque-transmitting devices are selectively engageable incombinations of two to yield at least eight forward speed ratios and atleast one reverse speed ratio.

A variety of speed ratios and ratio spreads can be realized by suitablyselecting the tooth ratios of the planetary gear sets.

The above features and other features and advantages of the presentinvention are readily apparent from the following detailed descriptionof the best modes for carrying out the invention when taken inconnection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 a is a schematic representation of a powertrain including aplanetary transmission in accordance with the present invention;

FIG. 1 b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 1 a; and

FIG. 1 c is a schematic representation of the powertrain of FIG. 1 adepicted in lever diagram form.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to the drawings, there is shown in FIG. 1 a a powertrain 10having a conventional engine and torque converter 12, a planetarytransmission 14, and a conventional final drive mechanism 16. The engine12 may be powered using various types of fuel to improve the efficiencyand fuel economy of a particular application. Such fuels may include,for example, gasoline; diesel; ethanol; dimethyl ether; etc.

The planetary transmission 14 includes an input member 17 continuouslyconnected with the engine 12, a planetary gear arrangement 18, and anoutput member 19 continuously connected with the final drive mechanism16. The planetary gear arrangement 18 includes four planetary gear sets20, 30, 40 and 50.

The planetary gear set 20 includes a sun gear member 22, a ring gearmember 24, and a planet carrier assembly member 26. The planet carrierassembly member 26 includes a plurality of pinion gears 27 rotatablymounted on a carrier member 29 and disposed in meshing relationship withboth the sun gear member 22 and the ring gear member 24.

The planetary gear set 30 includes a sun gear member 32, a ring gearmember 34, and a planet carrier assembly member 36. The planet carrierassembly member 36 includes a plurality of pinion gears 37 rotatablymounted on a carrier member 39 and disposed in meshing relationship bothwith the ring gear member 34 and the sun gear member 32.

The planetary gear set 40 includes a sun gear member 42, a ring gearmember 44, and a planet carrier assembly member 46. The planet carrierassembly member 46 includes a plurality of pinion gears 47 rotatablymounted on a carrier member 49 and are disposed in meshing relationshipwith both the sun gear member 42 and the ring gear member 44.

The planetary gear set 50 includes a sun gear member 52, a ring gearmember 54, and a planet carrier assembly member 56. The planet carrierassembly member 56 includes a plurality of pinion gears 57 rotatablymounted on a carrier member 59 and are disposed in meshing relationshipwith both the ring gear member 54 and the sun gear member 52.

The planetary gear arrangement also includes five torque-transmittingdevices 80, 82, 84, 85 and 86. The torque-transmitting devices 80 and 82are stationary-type torque-transmitting device, commonly termed reactionclutches or brakes. The torque-transmitting devices 84, 85 and 86 arerotating-type torque-transmitting devices, commonly termed clutches.

The input member 17 is continuously connected with the planet carrierassembly member 26 of the planetary gear set 20. The output member 19 iscontinuously connected with the planet carrier assembly member 36 of theplanetary gear set 30. The sun gear member 22 of the planetary gear set20 is continuously connected with the transmission housing 60.

A first interconnecting member 70 continuously connects the ring gearmember 24 of the planetary gear set 20 with the sun gear member 32 ofthe planetary gear set 20. A second interconnecting member 72continuously connects the ring gear member 34 of the planetary gear set30 with the planet carrier assembly member 46 of the planetary gear set40 and with the ring gear member 54 of the planetary gear set 50. Athird interconnecting member 74 continuously connects the ring gearmember 44 of the planetary gear set 40 with the planet carrier assemblymember 56 of the planetary gear set 50.

A first torque-transmitting device, such as brake 80, selectivelyconnects the sun gear member 42 of the planetary gear set 40 with thetransmission housing 60. A second torque-transmitting device, such asbrake 82, selectively connects the ring gear member 44 of the planetarygear set 40 with the transmission housing 60. A thirdtorque-transmitting device, such as clutch 84, selectively connects theplanet carrier assembly member 26 of the planetary gear set 20 with thering gear member 44 of the planetary gear set 40. A fourthtorque-transmitting device, such as clutch 85, selectively connects thering gear member 24 of the planetary gear set 20 and the sun gear member32 of the planetary gear set 30 via interconnecting member 70 with thesun gear member 52 of the planetary gear set 50. A fifthtorque-transmitting device, such as clutch 86, selectively connects theplanet carrier assembly member 36 of the planetary gear set 30 with thesun gear member 52 of the planetary gear set 50.

As shown in FIG. 1 b, and in particular the truth table disclosedtherein, the torque-transmitting devices are selectively engaged incombinations of two to provide at least eight forward speed ratios andat least one reverse speed ratio all with single transition sequentialshifts, and including two overdrive ratios.

As set forth above, the engagement schedule for the torque-transmittingdevices is shown in the truth table of FIG. 1 b. The chart of FIG. 1 bdescribes the gear ratios and ratio steps that are attained in the abovedescribed transmission. For example, the step ratio between the firstand second forward speed ratios is 1.46, while the step ratio betweenthe reverse speed ratio and first forward ratio is −0.73.

Referring to FIG. 1 c, the embodiment of powertrain 10 depicted in FIG.1 a is illustrated in a lever diagram format. A lever diagram is aschematic representation of the components of a mechanical device suchas an automatic transmission. Each individual lever represents aplanetary gearset, wherein the three basic mechanical components of theplanetary gear are each represented by a node. Therefore, a single levercontains three nodes: one for the sun gear member, one for the planetgear carrier member, and one for the ring gear member. The relativelength between the nodes of each lever can be used to represent thering-to-sun ratio of each respective gearset. These lever ratios, inturn, are used to vary the gear ratios of the transmission in order toachieve appropriate ratios and ratio progression. Mechanical couplingsor interconnections between the nodes of the various planetary gear setsare illustrated by thin, horizontal lines and torque transmittingdevices such as clutches and brakes are presented as interleavedfingers. If the device is a brake, one set of the fingers is grounded.Further explanation of the format, purpose and use of lever diagrams canbe found in SAE Paper 810102, authored by Benford, Howard and Leising,Maurice, “The Lever Analogy: A New Tool in Transmission Analysis”, 1981,which is hereby fully incorporated by reference.

The powertrain 10 includes an input member 17 continuously connectedwith the engine 12, an output member 19 continuously connected with thefinal drive 16, a first planetary gear set 20A having three nodes: afirst node 22A, a second node 26A and a third node 24A; a secondplanetary gear set 30A having three nodes: a first node 32A, a secondnode 36A and a third node 34A; a third planetary gear set 40A havingthree nodes: a first node 42A, a second node 46A and a third node 44A;and a fourth planetary gear set 50A having three nodes: a first node52A, a second node 56A and a third node 54A.

The input member 17 is continuously connected with the node 26A and theoutput member 19 is continuously connected with the node 36A. The node22A is continuously connected with the transmission housing 60.

The node 24A is continuously connected with the node 32A. The node 34Ais continuously connected with the nodes 46A and 54A. The node 44A iscontinuously connected with the node 56A.

A first torque-transmitting device, such as brake 80, selectivelyconnects the node 42A with the transmission housing 60. A secondtorque-transmitting device, such as brake 82, selectively connects thenode 44A with the transmission housing 60. A third torque-transmittingdevice, such as clutch 84, selectively connects the node 26A with thenodes 44A and 56A. A fourth torque-transmitting device, such as clutch85, selectively connects the nodes 24A and 32A with the node 52A. Afifth torque-transmitting device, such as clutch 86, selectivelyconnects the node 36A with the node 52A.

To establish ratios, two torque-transmitting devices are engaged foreach gear state. The engaged torque-transmitting devices are representedby an “X” in each respective row in FIG. 1 b. For example, to establishreverse gear, the brake 82 and clutch 85 are engaged. The brake 82engages the node 44A with the transmission housing 60. The clutch 85engages the nodes 24A and 32A with the node 52A. Likewise, the eightforward ratios are achieved through different combinations of clutchengagement as per FIG. 1 b.

The powertrain 10 may share components with a hybrid vehicle, and such acombination may be operable in a “charge-depleting mode”. For purposesof the present invention, a “charge-depleting mode” is a mode whereinthe vehicle is powered primarily by an electric motor/generator suchthat a battery is depleted or nearly depleted when the vehicle reachesits destination. In other words, during the charge-depleting mode, theengine 12 is only operated to the extent necessary to ensure that thebattery is not depleted before the destination is reached. Aconventional hybrid vehicle operates in a “charge-sustaining mode”,wherein if the battery charge level drops below a predetermined level(e.g., 25%) the engine is automatically run to recharge the battery.Therefore, by operating in a charge-depleting mode, the hybrid vehiclecan conserve some or all of the fuel that would otherwise be expended tomaintain the 25% battery charge level in a conventional hybrid vehicle.It should be appreciated that a hybrid vehicle powertrain is preferablyonly operated in the charge-depleting mode if the battery can berecharged after the destination is reached by plugging it into an energysource.

While the best modes for carrying out the invention have been describedin detail, those familiar with the art to which this invention relateswill recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

1. A multi-speed transmission comprising: an input member; an outputmember; first, second, third and fourth planetary gear sets each havingfirst, second and third members; a first interconnecting membercontinuously connecting said third member of said first planetary gearset with said first member of said second planetary gear set; a secondinterconnecting member continuously connecting said third member of saidsecond planetary gear set with said second member of said thirdplanetary gear set and with said third member of said fourth planetarygear set; a third interconnecting member continuously connecting saidthird member of said third planetary gear set with said second member ofsaid fourth planetary gear set; said first member of said firstplanetary gear set being continuously connected with a stationarymember; and five torque transmitting devices for selectivelyinterconnecting said members of said planetary gear sets with othermembers of said planetary gear sets, or with said stationary member,said five torque-transmitting devices being engaged in combinations oftwo to establish at least eight forward speed ratios and at least onereverse speed ratio between said input member and said output member. 2.The transmission of claim 1, wherein a first of said fivetorque-transmitting devices is operable for selectively connecting saidfirst member of said third planetary gear set with said stationarymember.
 3. The transmission of claim 2, wherein a second of said fivetorque-transmitting devices is operable for selectively connecting saidthird member of said third planetary gear set with said stationarymember.
 4. The transmission of claim 3, wherein a third of said fivetorque-transmitting devices is operable for selectively connecting saidsecond member of said first planetary gear set with said third member ofsaid third planetary gear set.
 5. The transmission of claim 4, wherein afourth of said five torque-transmitting devices is operable forselectively connecting said third member of said first planetary gearset with said first member of said fourth planetary gear set.
 6. Thetransmission of claim 5, wherein a fifth of said fivetorque-transmitting devices is operable for selectively connecting saidsecond member of said second planetary gear set with said first memberof said fourth planetary gear set.
 7. The transmission defined in claim1, wherein two of said five torque-transmitting devices comprise brakes;and the other three of said five torque-transmitting devices compriseclutches.
 8. The transmission of claim 1, wherein said first, second andthird members of said first, second, third and fourth planetary gearsets comprise a sun gear member, a planet carrier assembly member and aring gear member, respectively.
 9. The transmission of claim 1, whereinsaid input member is continuously interconnected with said second memberof said first planetary gear set, and said output member is continuouslyinterconnected with said second member of said second planetary gearset.
 10. A multi-speed transmission comprising: an input member; anoutput member; first, second, third and fourth planetary gear sets eachhaving first, second and third members; said input member beingcontinuously interconnected with said second member of said firstplanetary gear set; said output member being continuously interconnectedwith said second member of said second planetary gear set; said firstmember of said first planetary gear set being continuously connectedwith a stationary member; a first interconnecting member continuouslyconnecting said third member of said first planetary gear set with saidfirst member of said second planetary gear set; a second interconnectingmember continuously connecting said third member of said secondplanetary gear set with said second member of said third planetary gearset and with said third member of said fourth planetary gear set; athird interconnecting member continuously connecting said third memberof said third planetary gear set with said second member of said fourthplanetary gear set; a first torque-transmitting device selectivelyconnecting said first member of said third planetary gear set with saidstationary member; a second torque-transmitting device selectivelyconnecting said third member of said third planetary gear set with saidstationary member; a third torque-transmitting device selectivelyconnecting said second member of said first planetary gear set with saidthird member of said third planetary gear set; a fourthtorque-transmitting device selectively connecting said third member ofsaid first planetary gear set with said first member of said fourthplanetary gear set; a fifth torque-transmitting device selectivelyconnecting said second member of said second planetary gear set withsaid first member of said fourth planetary gear set; and saidtorque-transmitting devices being engaged in combinations of two toestablish at least eight forward speed ratios and at least one reversespeed ratio between said input member and said output member.
 11. Amulti-speed transmission comprising: an input member; an output member;first, second, third and fourth planetary gear sets each having a sungear member, planet carrier assembly member and ring gear member; saidinput member being continuously interconnected with said planet carrierassembly member of said first planetary gear set; said output memberbeing continuously interconnected with said planet carrier assemblymember of said second planetary gear set; said sun gear member of saidfirst planetary gear set being continuously connected with a stationarymember; a first interconnecting member continuously connecting said ringgear member of said first planetary gear set with said sun gear memberof said second planetary gear set; a second interconnecting membercontinuously connecting said ring gear member of said second planetarygear set with said planet carrier assembly member of said thirdplanetary gear set and with said ring gear member of said fourthplanetary gear set; a third interconnecting member continuouslyconnecting said ring gear member of said third planetary gear set withsaid planet carrier assembly member of said fourth planetary gear set; afirst torque-transmitting device selectively connecting said sun gearmember of said third planetary gear set with said stationary member; asecond torque-transmitting device selectively connecting said ring gearmember of said third planetary gear set with said stationary member; athird torque-transmitting device selectively connecting said planetcarrier assembly member of said first planetary gear set with said ringgear member of said third planetary gear set; a fourthtorque-transmitting device selectively connecting said ring gear memberof said first planetary gear set with said sun gear member of saidfourth planetary gear set; a fifth torque-transmitting deviceselectively connecting said planet carrier assembly member of saidsecond planetary gear set with said sun gear member of said fourthplanetary gear set; and said torque-transmitting devices being engagedin combinations of two to establish at least eight forward speed ratiosand at least one reverse speed ratio between said input member and saidoutput member.